Fluid motor with selective displacement



July 9, 1968 A. A. SCHMITZ FLUID MOTOR WITH SELECTIVE DISPLACEMENT Original Filed Aug. 27, 1964 2 Sheets-Sheet 1 INVENTO/Z AL EFT A. 5% Arm 8 July 9, 1968 A. A. SCHMITZ FLUID MOTOR WITH SELECTIVE DISPLACEMENT Original Filed Aug. 27, 1964 2 Sheets-Sheet 2 United States Patent 3,391,609 FLUID MOTGR WITH SELECTIVE DISPLACEMENT Albert A. Schmitz, 5217 Durand Ave., Racine, Wis. 53406 Original application Aug. 27, 1964, Ser. No. 392,392. Divided and this application Dec. 2, 1966, Ser. No.

11 Claims. e1. 91-73 ABSTRAQT OF THE DISL0URE A reversible vane type fluid motor in which a sliding valve element is utilized to alter the displacement by cutting off a sequence of the inlet passageways in the stator from the pressurized fluid supply and connecting them to the return fluid conduit thus forcing all energized fluid to pass through the remaining inlet passageways to selected pressure chambers.

This application is a division of applicants co-pending application, Ser. No. 392,392, filed Aug. 27, 1964, and entitled, Fluid Power Converter.

This invention relates to a fluid motor and more specifically relates to a fluid motor of the radial vane variety permitting the development of high torque. An important objective of this invention is to provide an efficient fluid translating device having a high torque-to-weight ratio wherein said device can be manufactured with a compactness and economy not known to the hydraulic arts.

A still further objective of this invention is to provide a fluid translating device adaptable in manufacture for low or high power requirements while maintaining the same basic construction and avoiding the high costs inherent in machines having close tolerances normally associated with capabilities of this nature.

Another important objective of this invention is to provide a multi-speed fluid motor wherein a constant level of volume input fluid is utilized to produce more than one output speed.

A still further objective of the invention is to provide a novel annular rotor assembly comprising a plurality of loose segments held together by a tight fitting ring in a manner defining a plurality of channels for the reception of floating vanes. In furtherance of this objective the invention also provides a fluid translating device in which the above-mentioned vane channels can be alternatively machined along the inner face of an annular rotor.

Another important objective of the invention is to provide a fluid translating device wherein an annular rotor is manufactured of a rigid, low-friction material and is retained in position by an external ring of high tensile strength.

A principal and main objective of this invention is to provide a hydraulic unit of the type described wherein one or a series of separate brace members are disposed in spaced relationship along each of the vane channels .and the vanes receivable in the channels are notched accordingly to receive the braces. With this arrangement the vanes are reciprocated within the channels a full stroke while the bracing members prevent the pinching of vanes in adjacent channels due to the hydraulic pressures in adjacent channels.

Primarily, this invention finds itself in the field of rotary, vane-type fluid motors and pumps. This field of fluid translators can basically be divided into two major groups; namely, (1) those translators wherein an annular stator member is contoured with an irregular inner surface and surrounds a rotating inner rotor having channels in which radially extending vanes are in sliding contact 3,391,669 Patented July 9, 1968 with the irregular surface, and (2) those fluid translators wherein the inner member is stationary and the outer annular member is the rotor and has vane-receiving channels formed therein. In either classification the vanes must reciprocate freely within their channels. If high pressure against one vane squeezes or distorts the adjacent channel, reciprocation of the adjacent vane becomes difficult, and an ineflicient fluid translator is the result. A conventional solution is to provide ample clearance between the vane and channel so that the sides of the channel can collapse somewhat before binding. The result is a noisy operation and an increase in inefiiciency, especially when a two-edged vane of the type described hereinafter is used.

Therefore, an important and principal objective of this invention is to provide a rotor wherein all the vane receiving channels are braced against collapse and dis tortion by braces which provide a clearance for the vanes without subtracting from the radial dimension of the vane to thereby provide a vane having adequate proportions and at the same time received in channels permitting a full reciprocating stroke.

Another important objective of the invention is to provide a rotor assembly which can be economically manufactured while providing means for maintaining control of the width of the vane slots to thereby permit a close fitting vane which operates more efficiently and quietly than loose fitting vanes which are more common in the art.

A still further objective of the invention is to provide a fluid pump or motor with a stator or rotor having a large, even number of lobes forming displacement chambers, in which each pair of diametrically opposed chambers have inlet or exhaust passages axially spaced from passages in other pairs of displacement chambers to thereby permit a selection of combinations of passages and active displacement chambers for producing various capacities and speeds from the same volume of input fluid. In this manner the entire unit remains in hydrostatic balance regardless of the combination selected.

A further objective is to provide a fluid pump or motor having a stator or rotor carrying closely spaced slidable vanes making possible higher torque by means of a greater number of reaction lobes on the opposing rotor or stator.

In summary, therefore, the invention provides a fluid converter wherein a brace or braces are positioned within vane receiving channels which braces permit the use of a large number of closely spaced vanes. With a large number of closely spaced vanes an increased number of reaction lobes can be used for obtaining additional torque. In turn the additional lobes make feasible the use of a greater number of axially spaced pairs of inlet and outlet passages for better speed selection and range of speed control.

These and other important objectives and advantages of the invention will be more fully understood upon a reading of the following specifications taken in view of the attached drawings wherein:

FIGURE 1 is a longitudinal cross-sectional view of the device;

FIGURE 2 is a cross-sectional view taken along the line 22 in FIGURE 1;

FIGURE 3 is a cross-sectional view taken along the line 33 of FIGURE 1; and

FIGURE 4 is a partial perspective of the interior of the device with portions broken away.

Referring now with more particularity to the drawings where like numerals indicate like parts, the numeral 10 indicates the housing of this invention. The housing 10 includes a pair of end plates 12 and 14 which define a chamber 16 therebetween. The plates are spaced from one another via a plurality of segments 18 which are threadedly bored at 20. The plates define a rotor housing 21. Each bore receives a bolt 22 for securing the end plates together. The two end plates are peripherally machined at 24 to receive an annular ring 26 which forms a cylindrical side wall of the chamber.

The segments 18 form a series of circumferentially arranged channels 28 therebetween. In the embodiment shown, the segments extend toward end plate 14 and are integral with the end plate 12. It should be understood that the segments can be integral with the plate 14 or independent segments secured to both plates by bolts at either end. Each of the channels slidably receives a vane member 30. The vane members extend between end plates 12 and 14 and are formed with a groove 32 at their inner ends. The vanes along their outer ends are formed with a plurality of notches 34. Each of the vanes is bored at 36 and counterbored at 38. Each counterbore receives a spring biasing member 39. The springs 39 have one end engaging the inner surface of ring 26 and their other ends engaging ledges 41 at the bottoms of the counterbores 38. The vane is thereby normally 'biasedjo an engagement with the periphery of an interior stator member 40.

The stator member 40 is generally cylindrical and is formed with a contoured periphery 42 that has a maximum diameter substantially the same as the inner diameter of the circle defined by the inner surfaces 44 of the segments 18 and other diameters of less dimension which form, with the segments, displacement chambers 48. In the known fashion, as fluid is delivered and exhausted from these displacement chambers, the pressure exerted causes the rotor housing 21 to rotate with respect to the stationary member 40.

The end plates 12 and 14 are respectively bored at 52 and 54 to receive a fluid delivery tubular member 56. When used with a vehicle, member 56 is load bearing in addition to functioning as a fluid delivery conduit. The length of member 56 at the break shown in FIG- URE 1 is of a suflicient length to provide a mounting area for securement to the vehicle or other machine. The end plates 12 and 14 and the apparatus carried thereby are rotatably mounted with respect to member 56 via the raceways 57 and 58. The member 56 is secured longitudinally to the rotor by a nut 62 which engages the threads 64 formed at the inner end of the member 56.

Slidably received in member 56 is a hollow operating shaft 65. In spaced concentric relationship with the shaft 65 between the shaft and member 56 is a sleeve 66. The sleeve is longitudinal fixed to the shaft by welds 67 at either end. The sleeve is formed with inwardly directed end flanges 68 and 69 which form with the shaft 66 and sleeve 65, a fluid transferring annulus 70. The sleeve is also formed with outwardly extending annular flanges 71, 72, 73 and 74 each in sealing and sliding engagement with the interior of the stationary tubular member 56. With the member 56, the flanges 71 and 72 form a porting annulus 63, the flanges 72 and 73 a porting annulus 75, and flanges 73 and 74 a porting annulus 76. The shaft assembly is moved longitudinally of the tubular member 56 via an operators handle 80 and the fulcrum lug 82.

The tubular member 56 is formed with a fluid inlet 84 in communication with the porting annulus 76 and fluid transferring annulus 70 via aperture 86 in the sleeve 66. Fluid introduced under pressure, through aperture 84 is communicated to the pressure passages 92 and 93 of the stator 40 via a plurality of apertures 91 formed in the sleeve housing and the porting annulus 76. Note that although all the exhaust passages 90 are in the same plane, inlet passages 92 and 93 are longitudinally spaced along the stator axis with respect to each other.

As will be well understood by those skilled in the art, as pressure is introduced into chambers 48, the rotor 21 will rotate, causing the vanes to reciprocate within their respective channels 28. In other Words, the pockets between the vanes in the chambers 48 are subjected to pressurized fluid as they pass the passages 92 and 93 and exhaust their fluid through the passages 90.

It should be noted that the flanges 73 and 74, as positioned in FIGURE 1, permit the fluid under pressure in the annulus 76 to enter all of the passages 92 and 93 of rotor 40. This fluid is exhausted through passages 90 into the porting annulus 75 and finally to the tank via outlet 95 of tubular member 56. With the handle pivoted counterclockwise from the position of FIG- URE 1, the sleeve or shaft is moved to the right and flange 73 assumes position M between chambers 92 and 93, cutting off passages 93 from pressurized fluid and communicating them to exhaust annulus 75. All pressurized fluid must now pass through passages 92 which are in communication with half of the displacement chambers. As also will be understood by those skilled in the art, by moving the sleeve in this manner, the rotor is caused to rotate at twice the speed but with only half the torque that is available in the FIGURE 1 position because of the decrease in displacement.

In other words, when shifting sleeve assembly 65-66 is moved to the right (Sec. 22) fluid passages 93 are cutofl from annulus 76 and connected to annulus 75. Since passages 93 are now in communication with passages through annulus 75 a free circulation of fluid can take place through the two displacement chambers 48 that are adjacent to passages 93. All working fluid is directed through the remaining two displacement chambers 48 adjacent to passages 92, thus causing the doubling of the rotational speed of annulus rotor housing 21.

When pressurized fluid is introduced through annulus 75 the direction of rotation is reversed but the speed remains the same since passages 93 are still common with 90 through 75. Only two displacement chambers 48 adjacent passages 92 are subjected to diflerential pressure.

It should be understood at this point that for ease of description purposes, the embodiment disclosed is of a four lobe two speed type but that due to the ability to substantially increase the number of vanes, the invention makes practicable to give the art an eight or more lobe, multi-speed (3 and above) translator. A greater number of speeds can be obtained by axially forming another set of passages along the length of the stator similar to passages 92 and 93.

The fluid translator of this invention is enclosed at the handle end by a cup-shaped member formed with an end portion 97 secured to the sleeve 66 by way of bolts 98. The member 96 in its skirt portion is formed with appropriate apertures to mate with the inlet opening 84 and the outlet opening 95 of tubular member 56. At its other end, the fluid translator is enclosed by way of a cap 99 secured to the plate 14 by way of bolts 100.

FIGURE 4 of the invention discloses the novel vane configuration which is of major significance to this invention. Critical to sliding vane operation is the width dimension W and its relationship with the recess depth D in which it reciprocates. Also of importance is the dimension T of the segment 18 because the sturdiness and thickness of this member is eflective as to the amount of pinching caused in adjacent channels due to a pressure transference. In order to reduce dimension T to a minimum, to permit a many-vaned pump, this invention teaches the use of spacer braces 35 within the channels to prevent any deflection of the member segments 18 which would pinch against the vanes 30 in adjacent slots. Normally, such spacers would so diminish the dimension D that the vane 30 would have an insuflicient width W to operate effectively. The utilization of notches 34 to receive the braces 35 permits the full dimension W of the vane to reciprocate freely in the slots and thus all features of an eflicient and compact machine are maintained.

It should be noted that the chordal distance A between the leading edge of the exhaust passage 90 and the trailing edge of the inlet passages 93 is less than the length of the inner dwell by at least the thickness of two vanes. This permits the relatively heavy vanes 30 to ride the fall surface of the stator completely to the lower dwell prior to absorbing any thrust. Also, it should be noted that the leading edge of the vane (see B in upper right-hand sector of FIG. 2) receives the thrust initially as it closes the pressure passage. The edge B is relieved of load as soon as the trailing edge C passes this point. The importance of the fit of the vanes 30 in their slots 28 is that both edges of the vanes must seal. Hence the vanes must not tilt in their slots.

A fluid seepage between the stator 40 and the side plates or between the stator and the member 56 is retained in the housing by the annular rotary seal 101. The stator is formed with a seepage passage 102 to permit all such leakage to reach the inner end of member 56 and flow through the hollow shaft 65 to discharge from the unit through holes 103 and external drain port 104. Clamping lugs L for attaching pneumatic tire rims or other devices are provided on the housing. In the embodiment shown the lugs are a part of ring 26. Ring 26 can be manufactured with any desired type of clamp or securing means without affecting the remaining elements of the invention.

It should be noted that one complete surface section of the four-lobed stator disclosed consists of (FIG. 2) the outer dwell surface, the inner dwell surface and the minimum acceleration surfaces 106 between the two dwell portions.

In a general manner, while there has been disclosed in the above description, what is deemed to be the most practical and eflicient embodiment of the invention, it should be well understood that the invention is not limited to such an embodiment as there might be changes made in the arrangement, disposition, and form of the parts without departing from the principle of the present invention as comprehended within the scope of the accompanying claims.

I claim:

1. In a fluid motor of a type having an inner element journaled within an outer component, said inner element being formed with a plurality of lobes and depressions defining a plurality of fluid chambers with said outer component, said outer component having channels slidably receiving vanes which move to a first position fully re cessed in said channels when cammed to this position by said lobes and to a second position projecting into said chambers for reaction with fluid therein when opposing said depressions, that improvement of a load bearing member fixedly secured to said inner element, fluid conducting means in said member for delivering pressurized fluid to the interior of said inner element, a plurality of passageways in said inner element for communicating said interior to said chambers, said inner element having outlet passageways for exhausting said chambers to the interior of said inner element and longitudinally slidable means in said member isolating said plurality of passageways from said outlet passageways.

2. In a fluid motor of a type having an inner, generally cylindrical stator journaled within an outer rotor, said stator being formed with an even number of lobes and depressions forming a plurality of fluid chambers with said rotor, said rotor having channels slidably receiving vanes which move to a first position fully recessed in said channels when cammed to this first position by said lobes and to a second position projecting into said chambers for reaction with fluid therein when opposing said depressions, that improvement of a load bearing and fluid conducting member fixedly secured to said stator, a plurality of inlets passageways in said load-bearing and fluid conducting member and in said stator in communication with said fluid chambers, at least one of said inlet passageways being spaced longitudinally along the axis of said stator from the other of said inlet passageways, said stator and said load-bearing and fluid-conducting member being formed with outlet passageways longitudinally spaced from said inlet passageways, and longitudinally slidable means carried by said load-bearing and fluid-conducting member for isolating said inlet passageways from said passageways and for selectively isolating at least one of said inlet passageways from the said other inlet. passageways.

3. In a fluid motor of a type having an inner, generally cylindrical stator journaled within an outer rotor, said stator being formed with an even number of lobes and depressions forming a plurality of fluid chambers with said rotor, said rotor having channels slidably receiving vanes which move to a first position fully recessed in said channels when cammed to this first position by said lobes and to a second position projecting into said chambers for reaction with fluid therein when opposing said depressions, that improvement of a load bearing and fluid conducting member fixedly secured to said stator, first and second pairs of inlet passageways in said stator in communication with said fluid chambers, and said first pair of inlet passageways being spaced longitudinally along the axis of said stator from the said second pair of inlet passageways, said stator being formed with outlet passageways longitudinally spaced from said inlet passageways, and longitudinally slidable means carried by the said load-bearing and fluid-conducting member for isolating said inlet passageways from said outlet passageways and for selectively isolating said first pair of inlet passageways from the said other pair of inlet passageways.

4. In a fluid motor of a type having an inner, generally cylindrical element journaled within an outer component, said inner element being formed with an even number of lobes and depressions forming a plurality of fluid chambers with said outer component, said outer component having channels slidably receiving vanes which move to a first position fully recessed in said channels when cammed to this first position by said lobes and to a second position projecting into said chambers for reaction with fluid therein when opposing said depressions, that improvement of a load-bearing and fluid-conducting member fixedly secured to said inner element, a first pair of inlet passageways in said inner element extending in opposite directions relative to each other and communicating with said fluid chambers, a second pair of inlet passageways in said inner element extending in opposite directions relative to each other and communicating with said fluid chambers, said first pair of inlet passageways being spaced longitudinally along the axis of said inner element from the said second pair of inlet passageways, said inner element formed with outlet passageways longitudinally spaced from said inlet passageways, and longitudinally slidable means isolating said inlet passageways from said outlet passageways and for selectively isolating said first pair of inlet passageways from the said other pair of inlet passageways.

5. A fluid motor comprising (a) an outer rotor;

(b) a load-bearing and fluid-conducting member;

(c) a stator within said outer rotor 1) secured to said load-bearing and fluid-conducting member axially thereof;

(d) cs1aid outer rotor and said stator cooperating to pro- (l) a plurality of chambers; (e) said stator having (1) a plurality of inlet passageways to the said chambers spaced from each other along the axis of the said stator; and said stator having (2) outlet passageways from the said chambers spaced axially of said stator from the said inlet passageways;

(i) said load-bearing and fluid-conducting member conducting pressurized fluid to the said inlet passageway; and

(g) longitudinally slidable means isolating said inlet passageways from the said outlet passageways and for selectively isolating at least one of said inlet passageways from the other inlet passageways.

6. A fluid motor comprising (a) a load-bearing and fluid-conducting member;

(b) an inner element; and

(c) an outer element both carried by said load-bearing and fluid-conducting member for rotation relative to each other; and forming (d) an annular fluid chamber therebetween (e) lobes and vanes carried by the said inner element and the said outlet element, respectively, and dividing the said fluid chamber into (1) pulsing sections;

(f) axially spaced channels in the said load-bearing and fluid-conducting member and in the said inner element for conducting fluid between the said load-bearing and fluid-conducting member and the said pulsing sections of the said annular fluid chamber; and

(g) longitudinally slidable means in the said load-bearing and fluid-conducting member for selectively isolating or establishing communication between the various said axially spaced channels in the said loadbearing and fluid-conducting member.

7. A fluid motor as defined in claim 6 in which (a) the said longitudinally slidable means cooperates with the said load-bearing and fluid-conducting member to form therewith,

(1) two annular fluid-conducting passageways;

and in which (b) the said longitudinally slidable means is adapted to be positioned to selectively register ditferent combinations of the said axially spaced channels with the said two annular fluid-conducting passageways.

8. A fluid motor comprising (a) a load-bearing and fluid-conducting member;

(b) an outer member;

(c) an inner member carried by said load-bearing and fluid-conducting member and having (1) lobes and depressions cooperating with the said outer member to define (2) a plurality of fluid chambers;

((1) primary passageways arranged in the same plane in the said load-bearing and fluid-conducting member and in the said inner member providing communication between the interior of the said loadbearing and fluid-conducting member and one side of the said lobes carried by the said inner member;

(e) secondary passageways in the said load-bearing and fluid-conducting member and the said inner member and providing communication between the interior of the said load-bearing and fluid-conducting member and the side of the said lobes opposite from the said one side thereof;

(f) said secondary passageways being (1) arranged in pairs; and being (2) longitudinally spaced from each other and from the said primary passageways;

(g) longitudinally slidable valve means carried by the said load-bearing and fluid-conducting member and cooperating therewith to form (1) two annular chambers;

(h) one of said annular chambers serving to carry pressurized fluid to the said primary passageways or spent fluid therefrom;

(i) the other of said annular chambers having communication with the interior of the said longitudinally slidable valve means and serving to convey spent fluid from the said secondary passageways or pressurized fluid thereto; and

(j) said longitudinally slidable valve means being movable selectively to 1) separate the said secondary passageways from the said primary passageways; or

(2) to establish communication between one or more pairs of the said secondary passageways and the said primary passageways.

9. A fluid motor comprising (a) an outer rotor;

(b) a load-bearing and fluid-conducting member;

(c) a stator within said outer rotor and having (1) major and minor diameters;

(d) said outer rotor and said stator cooperating to provide ( 1) a plurality of chambers;

(e) two sets of passageways in said stator and in said load-bearing and fluid-conducting member spaced axially from each other, said passageways establishing communication between the interior of the loadbearing member and all of said chambers;

(f) one set of the said passageways lying in one plane and opening into the said chambers on the same radial side of the said chambers between the said major and minor diameters of said stator,

(g) the other set of the said passageways entering each of said chambers on the opposite radial side of the said chambers between the said major and minor diameters of said stator;

(h) certain of the said passageways in the said second set of passageways being spaced axially from the other passageways in the said second set thereof; and

(i) longitudinally slidable means in the said load-bearing and fluid-conducting member for selectively isolating the said one set of passageways from the said other set of passageways and for selectively isolating at least one of the said passageways in the said second set of passageways from the other passageways in the said second set of passageways.

10. A fluid motor as defined in claim 9 in which (a) the said longitudinally slidable means is adapted to selectively combine one or more of the said passageways in the said second set of passageways with the passageways in the said first set of passageways.

11. A fluid motor as defined in claim 10 in which the longitudinally slidable means is further adapted to convey seepage fluid from the vicinity of the said stator and said rotor to a remote discharge port.

References Cited UNITED STATES PATENTS 615,664 12/1898 Dearing 91140 X 2,247,410 7/1941 Ross 9173 X 2,936,716 5/1960 Looker 103-12O 3,008,424 11/1961 Roth 103l21 3,241,456 3/1966 Wolfe 9l73 X 722,086 3/1903 Craig et a1. 91103 942,275 12/1909 Minue 91113 1,518,812 12/1924 Olson 91113 MARTIN P. SCHWADRON, Primary Examiner.

G. N. BAUM, Assistant Examiner. 

